EP1441139A2 - Frein contrôlé par couple - Google Patents

Frein contrôlé par couple Download PDF

Info

Publication number
EP1441139A2
EP1441139A2 EP04100153A EP04100153A EP1441139A2 EP 1441139 A2 EP1441139 A2 EP 1441139A2 EP 04100153 A EP04100153 A EP 04100153A EP 04100153 A EP04100153 A EP 04100153A EP 1441139 A2 EP1441139 A2 EP 1441139A2
Authority
EP
European Patent Office
Prior art keywords
brake
disc
friction surface
cam part
surface means
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP04100153A
Other languages
German (de)
English (en)
Other versions
EP1441139B1 (fr
EP1441139A3 (fr
Inventor
Ismo Kuivamäki
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Konecranes PLC
Original Assignee
KCI Konecranes PLC
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by KCI Konecranes PLC filed Critical KCI Konecranes PLC
Publication of EP1441139A2 publication Critical patent/EP1441139A2/fr
Publication of EP1441139A3 publication Critical patent/EP1441139A3/fr
Application granted granted Critical
Publication of EP1441139B1 publication Critical patent/EP1441139B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D59/00—Self-acting brakes, e.g. coming into operation at a predetermined speed
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D5/00—Braking or detent devices characterised by application to lifting or hoisting gear, e.g. for controlling the lowering of loads
    • B66D5/02—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes
    • B66D5/12—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes with axial effect
    • B66D5/14—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes with axial effect embodying discs

Definitions

  • the invention relates to a torque controlled brake arranged between a drive shaft and a driven shaft, said brake comprising a brake disc/clutch disc arrangement arranged between the drive shaft and the driven shaft and comprising a first disc that is axially movingly but non-rotatably arranged on the driven shaft and a second disc that is axially movingly arranged between the first disc and the drive shaft, a first set of friction surface means arranged between the first disc and the second disc, a second set of friction surface means arranged between the second disc and a body of the brake, a spring arrangement arranged to axially press the discs and the friction surface means co-operating therewith against each other in order to achieve a braking engagement, and cam means arranged between the drive shaft and the brake disc/clutch disc arrangement, said means comprising a first cam part that is non-rotatably fastened to the drive shaft and a second cam part that is non-rotatably arranged on the second disc, the cam means causing by the impact of torque and rotation of the drive shaft and
  • Such a brake is disclosed in Finnish patent application 20010714.
  • a particular aim has been to better control the loads from the direction of the load in order to avoid safety risks.
  • What has also been attempted to avoid is the acceleration of the motor over the synchronous speed caused by the oscillation of the load.
  • Another object has been to expand the applications of the brake.
  • a substantial feature of this prior art solution is the use of two brake wheels, whereby the torques achieved with such wheels have been differently adjusted. This has enabled to customize the brake for various purposes and to provide the brake with additional properties, which previously have required specific arrangements.
  • the structure should allow combining different functions in a more diversified manner.
  • a brake according to the invention characterized in that the second disc is axially movingly arranged in relation to the second cam part, and that a third set of friction surface means is arranged between the second cam part and the first disc in order to move the torque from the drive shaft to the driven shaft.
  • the invention is based on a second brake disc/clutch disc, which moves more freely than previously, and whose course of motion can be adjusted such that the brake can always be opened against the brake torque by means of additional friction surfaces arranged for this purpose, thus ensuring the opening of the brake (the operation of the cam means) always when the brake should be opened.
  • flywheel mass is also arranged at the second disc, for instance by means of a separate coupling wheel, on which the second disc and preferably also the third set of friction surface means are arranged, for instance a load torque affecting an input shaft of the hoisting gear forces the driven wheel, when the drive force driving the hoisting gear ends, for instance when the current of an electric motor is switched off, to accelerate at first the flywheel mass and then the actuator, such as a rotor of an electric motor.
  • the actuator such as a rotor of an electric motor.
  • the appropriate dimensions of the structure allow providing such a torque remaining after the flywheel mass that is unable to open the brake. In a hoisting apparatus this is a very important feature that enables to avoid the load from descending or from abruptly falling, for instance if malfunction or failure occurs in the actuator. In such an unexpected situation, as well as during the end of a normal hoisting procedure, braking is smooth on account of such a structure, and abrupt heavy dynamic loads directed at the braking system are avoided.
  • the brake according to the invention can also easily be provided with a sliding clutch required in chain hoists, if desired.
  • the body of the brake comprises two parts, which are axially adjustable in relation to one another, whereby the position or the point of action of the second set of friction surface means can be adjusted and limited by means of a second body part.
  • the torque of the clutch and the brake is provided using the same spring force of the spring arrangement and the ratio between the two is handled by selecting the ratio of corresponding friction surfaces to be the same as the ratio between the clutch torque and the brake torque.
  • This arrangement provides such an advantage that when the torque of a sliding clutch is being adjusted, the torque of the brake changes at the same time in correct relation to the clutch torque.
  • the clutch torque can be adjusted while the actuator rotates, in the simplest form by rotating the second body part of the brake, thus also providing the clutch with a precisely correct adjustment, since only a dynamic friction coefficient is employed during adjustment.
  • the spring arrangement preferably comprises a spring array pressing the first disc towards the second cam part, and a second spring array pressing the first cam part towards the second cam part, and that the spring force of the first spring array is considerably greater than the spring force of the second spring array.
  • the second spring array centres the cam parts in relation to one another and the force thereof is selected such that it does not excessively reduce the actual spring force of the first spring array providing the brake torque.
  • the play in the first spring array also compensates for the wear of the friction surfaces.
  • a torque controlled brake 1 according to the invention is shown that is arranged between a chain hoist 2 and a hand-operated hoist 3.
  • a rotor 4 of the hand-operated hoist 3 operates as a drive shaft of the system.
  • the brake 1 comprises firstly cam parts 5 and 6, the first one of which indicated with reference numeral 5 is non-rotatably fastened to the rotor 4, while the second cam part 6 is rotatably and axially movingly arranged on an input shaft 7 of the chain hoist 2, the input shaft functioning as the driven shaft of the system, in other words as the shaft driving the chain hoist 2 and provided with driving force from the rotor 4 of the hand-operated hoist 3.
  • a coupling wheel 8 is non -rotatably and axially non-movingly fastened to the second cam part 6 for providing flywheel mass to the described system.
  • a brake disc/clutch disc arrangement is arranged between the cam parts 5 and 6, i.e. between the rotor 4 and the input shaft 7 of the chain hoist 2, the arrangement comprising a first disc 9 that is axially movingly but non-rotatably arranged on the input shaft 7, and a second disc 10 that is axially movingly but non-rotatably arranged on the coupling wheel 8 using pins 11 fastened on the periphery of the coupling wheel 8 through which the second disc 10 is thus at the same time fastened to the second cam part 6.
  • a spring arrangement 15, 16 that presses said components 9, 10, 12 and 14 against one another.
  • a spring arrangement comprises a first spring array 15, which is arranged between a bearing 17 of the input shaft 7 and the first disc 9 to press the first disc 9 towards the second cam part 6, and a second spring array 16 between a body 13 of the brake and a bearing 18 of the first cam part 5 pressing the first cam part 5 towards the second cam part 6.
  • the spring force of the first spring array 15 is considerably greater than the spring force of the second spring array 16.
  • the spring force of the second spring array should be selected such that it does not excessively reduce the actual spring force provided by the first spring array 15 providing the brake torque.
  • the play of the second spring array 16 forms the wear margin of the friction surface means 12, 14 and 19.
  • a third set of friction surface means 19 is by means of the coupling wheel 8 mounted on the second cam part 6, said means being placed non-movably in relation to the coupling wheel 8 and the second cam part 6 and arranged to co-operate with the first disc 9 in order to move the torque from the drive shaft, or the rotor 4, to the driven shaft, or to the input shaft 7 of the chain hoist 2.
  • the third set of friction surface means 19 can naturally also be fastened to the first disc 9 without changing the idea or operation thereof in anyway.
  • the third set of friction surface means 19 may also operate in order to provide a braking engagement.
  • the effective diameter of the third set of friction surface means is smaller than the corresponding measure of the first and second set of friction surface means 12 and 14. This is not necessarily the case, but the location of the third set of friction surface means 19 sets the limits for the dimensions thereof.
  • the cross section of both cam parts 5 and 6 is circular and comprises preferably kidney-shaped grooves 20 in the circumferential direction, the grooves being provided with a deep spot 22 in the middle in respect of a surrounding contact area 21 and low spots 23 at the ends, in which case the opposed cam parts 5 and 6 are connected to one another through the opposed grooves 20 and a ball 24 placed between each opposed pair of grooves.
  • the cam parts 5 and 6 cause by impact of torque and rotation of the rotor 4 and countertorque (of the brake torque) of the input shaft 7 to change the axial position between the discs 9 and 10 and the friction surface means 12, 14 and 19 in order to detach at least partly the braking engagement against the power caused by the spring arrangement 15, 16 and at the same time to provide an engagement transferring the torque between the first disc 9 and the coupling wheel 8 using the third set of friction surface means 19 as will be explained in more detail below.
  • the body 13 of the brake comprises two parts 25, 26 to be axially adjusted in relation to one another, whereby the adjustability is implemented using a thread arrangement 27 between the parts 25 and 26 so that the second set of friction surface means 14 is fastened to the second disc 10, which is pressed against a third disc 28 that is axially movingly but non-rotatably arranged on the first body part 25 by means of pins 29 circularly arranged thereto, and the axial motion of the second disc 10, the second set of friction surface means 14 and the third disc 28 in the direction of the braking power, or towards the body part 26, is restricted and can be adjusted using the second body part 26 (the "cover part" of the brake) supporting the first cam part 5.
  • the axially moving fastening of the third disc 28 can naturally be implemented also to the second body part 26, if it is structurally advantageous.
  • the adjustability between the body parts 25, 26 allowing the slidable clutch function is not necessary in all the applications of the invention. The adjustment in question and the effect thereof on the operation of the brake will be described below.
  • Figures 1 and 3 show the hoisting apparatus 2 in uncased form, but in practice the apparatus is naturally placed in an appropriate case (cf. for instance the structure in Figure 6), on which the components thereof can be supported and in which the required lubricant can be placed.
  • the most essential features of the invention are the axially moving second disc 10 of the brake disc/clutch disc arrangement, the flywheel mass provided by means of the coupling wheel 8 between the input shaft 7 and the cam parts 5, 6 and the torque achieved with the third set of friction surface means 19 in order to move the driving force from the rotor 4 to the input shaft 7.
  • the axial adjustability of the second set of friction surfaces 14 is essential as well.
  • Figure 1 shows a situation, in which a load 30 hanging from the chain hoist 2 rests upon the brake 1.
  • a situation occurs for instance when the rotation of the hand-operated hoist 3 is ended (or if it is damaged for some reason), in which case the second spring array 16 presses the first disc 9 and the first set of friction surface means 12 thereof against the second disc 10, which in turn by means of the second set of friction surface means 14 thereof sliding in the pins 11 is pressed towards the third disc 28, the motion of which the second body part 26 restricts and stops.
  • Braking takes place rapidly, but still smoothly, since the second disc 10 together with the coupling wheel 8 ensures that the flywheel masses of the system are also slowed down during braking. If the brake were not used to decelerate the flywheel masses, the load would decelerate on the entire brake torque. In such a case the braking would occur too rapidly and an extremely high dynamic strain would be placed upon the components carrying the load.
  • the torque of the rotor 4 allows opening the brake only so much that the load torque barely surpasses the brake torque.
  • the potential energy of the load is passed as friction work as heat to the friction surface means 12 and 14. This energy can be transferred for instance to the oil placed in the case formed of the body 3 of the brake.
  • the oil may simultaneously be the oil of the hoisting apparatus, as shown in the embodiment described below in Figure 5.
  • a sliding clutch whose structure and advantages achieved therewith have been explained above, required in the chain hoist is connected to the brake.
  • the torque of the clutch and the brake is provided using the same spring force of the spring array 15, 16 and the ratio between the two is attended to by selecting the ratio of corresponding friction surfaces, i.e. the friction surface means 12, 14 and 19, to be the same as the ratio between the clutch torque and the brake torque.
  • This arrangement provides such an advantage that when the torque of the sliding clutch is being adjusted, the brake torque changes at the same time in correct ratio as regards the clutch torque.
  • the clutch torque can be adjusted when rotating the rotor 4 by revolving the second body part 26 and after finding the correct adjustment locking it in position for instance with screws, thus also providing the precisely correct adjustment of the clutch, since only a dynamic friction coefficient is used during adjustment.
  • Figure 1 shows that the distance between a support surface 31 on the second body part 26 of the second spring array 17 and the coupling wheel 8 remains constant during the adjustment, and therefore only the torque of the first spring array 15 and the clutch and the brake change when the sliding clutch is adjusted.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)
EP04100153A 2003-01-22 2004-01-20 Frein contrôlé par couple Expired - Fee Related EP1441139B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI20030099 2003-01-22
FI20030099A FI114503B (fi) 2003-01-22 2003-01-22 Momenttiohjatusti toimiva jarru

Publications (3)

Publication Number Publication Date
EP1441139A2 true EP1441139A2 (fr) 2004-07-28
EP1441139A3 EP1441139A3 (fr) 2005-03-30
EP1441139B1 EP1441139B1 (fr) 2007-05-02

Family

ID=8565408

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04100153A Expired - Fee Related EP1441139B1 (fr) 2003-01-22 2004-01-20 Frein contrôlé par couple

Country Status (8)

Country Link
US (1) US7077245B2 (fr)
EP (1) EP1441139B1 (fr)
JP (1) JP3802533B2 (fr)
KR (1) KR100593742B1 (fr)
CN (1) CN1327147C (fr)
DE (1) DE602004006173T2 (fr)
ES (1) ES2282795T3 (fr)
FI (1) FI114503B (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8196720B2 (en) * 2006-01-10 2012-06-12 D-Brake Llc Brake apparatus and method
KR100965048B1 (ko) 2008-01-28 2010-06-21 왕현민 토크 구동 장치
DE102008021105A1 (de) * 2008-04-28 2009-10-29 Auma Riester Gmbh & Co. Kg Mechanische Bremse
US8215471B2 (en) * 2008-04-28 2012-07-10 Auma Riester Gmbh & Co. Kg Mechanical brake
US8246010B2 (en) * 2009-08-13 2012-08-21 Hess Daniel L Fluid shear actuated hoist brake
US8448922B2 (en) * 2009-09-25 2013-05-28 The Rowland Company Safety brake device for theatre hoist
DE102017120490A1 (de) * 2017-09-06 2019-03-07 Liebherr-Components Biberach Gmbh Freifallwinde
CN110985434B (zh) * 2019-11-29 2020-12-08 江苏中苏智能制造有限公司 一种具有离合保护结构的混流泵
CN110989705A (zh) * 2019-12-18 2020-04-10 青岛工和自动化设备有限公司 一种恒扭力控制器

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI10714A (fi) 1925-05-23 Jäähdyttäjä ilmakulkuneuvoja varten

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1635708A (en) * 1924-04-08 1927-07-12 Skf Svenska Kullagerfab Ab Front wheel brake for automobiles and the like
US3313381A (en) * 1964-07-02 1967-04-11 Borg Warner Electro-magnetic braking system
US3332525A (en) * 1965-08-25 1967-07-25 Dresser Ind Friction brake and reversing control for electric hoists
US3399867A (en) * 1966-10-28 1968-09-03 Eaton Yale & Towne Weston brake hoist construction
US3433332A (en) * 1967-04-07 1969-03-18 Eaton Yale & Towne Hoist overload preventing device
US3825100A (en) * 1972-06-14 1974-07-23 Eaton Corp Hoist with constant pressure one way brake
JPS61197395A (ja) * 1985-02-27 1986-09-01 株式会社　キト− 電動チエ−ンブロツク
DE3725692A1 (de) * 1986-08-05 1988-02-25 Akebono Brake Ind Bremsvorrichtung
DE19507191C1 (de) * 1995-03-02 1996-10-02 Stahl R Foerdertech Gmbh Hebezeug mit einer durch die Bremse verstellbaren Kupplung
JP3151612B2 (ja) * 1997-06-04 2001-04-03 新日本ホイール工業株式会社 多板クラッチのクリープ防止装置
JP3096290B1 (ja) * 1999-06-07 2000-10-10 バイタル工業株式会社 過負荷防止装置付き巻上機
US6250438B1 (en) * 2000-01-28 2001-06-26 Yih Cherng Co., Ltd. Disc brake for a bicycle
FI115155B (fi) * 2001-04-05 2005-03-15 Kci Kone Cranes Int Oy Vääntömomentilla avautuva levyjarry
US6830141B1 (en) * 2003-05-23 2004-12-14 General Motors Corporation Friction-based clutch actuation system

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI10714A (fi) 1925-05-23 Jäähdyttäjä ilmakulkuneuvoja varten

Also Published As

Publication number Publication date
KR100593742B1 (ko) 2006-06-30
DE602004006173T2 (de) 2008-01-10
US7077245B2 (en) 2006-07-18
EP1441139B1 (fr) 2007-05-02
KR20040067997A (ko) 2004-07-30
ES2282795T3 (es) 2007-10-16
CN1521421A (zh) 2004-08-18
EP1441139A3 (fr) 2005-03-30
US20040168865A1 (en) 2004-09-02
CN1327147C (zh) 2007-07-18
FI114503B (fi) 2004-10-29
FI20030099A0 (fi) 2003-01-22
JP3802533B2 (ja) 2006-07-26
FI20030099A (fi) 2004-07-23
DE602004006173D1 (de) 2007-06-14
JP2004225908A (ja) 2004-08-12

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